Refrigeration system



Nov. 16, 1948; A. a. NEAWTON 2,454,263

I REFRIGERATION SYSTEM I Filed April 5. 194.3 v s Sheets-Sheet 1 attorney Nov. 16,1948.

"A. B. NEWTON 3 2,454,263

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1/9 4 Y I Lg, L.-' r attorney NOV. I A. B. NEWTQN REFRIGERATION SYSTEM Filed April s, 1943 s Sheath-Sheet 3 Snventor Patented Nov. 16, 1948 OFFICE REFRIGERATION SYSTEM 'Alwin B. Newton, Minneapolis, Minn., assignor to Minneapolis-Honeywell Regulator Company, Minneapolis, Minn., a corporation of Delaware Application April 5, 1943, Serial No. 481,795

11 Claims. (Cl. 62-8) 1 In many applications of refrigerating apparatus it is highly desirable to vary the capacity of the system. Numerous manners of accomplishing this have been proposed in the past but,

superheat of the refrigerant in the evaporator.

To this end, I apply a variable cooling effect to the thermostatic element of the thermostatic expansion valve by utilizing refrigerant from the system whose capacity is being controlled.

I prefer to accomplish this result by, in effect, providing an auxiliary evaporator for cooling the thermostatic element of the thermostatic expansion valve and supplying to such auxiliary evaporator a varying amount of refrigerant under the control of a valve means, which refrigerant is obtained from the liquid line of the system and, after it has passed through the auxiliary evaporator, returns to the suction side of the system.

It is th'erefore a further object of my invention to vary the capacity of a refrigeration system by cooling the bulb or thermostatic element of the thermostatic expansion valve to a variable degree by the use of a small auxiliary evaporator which obtains its refrigerant from the system under control. By providing such an auxiliary evaporator, it is possible to modulate the amount of auxiliary cooling supplied to the thermostatic element of the thermostatic expansion valve whereas, if refrigerant were merely fed into the main portion of the system at an intermediate position in the evaporator or just ahead of the thermostatic element of the expansion valve, it would be impossible to obtain a modulating action.

Another problem in connection with the operation of refrigeration systems is to'prevent overloading of such systems when they are first placed into operation and the load thereonis large. Various means of solving this problem have been theretofore proposed including such expedients as unloader valves, suction line valves, and the like. I propose, however, to accomplish this result by varying the superheat setting of 2 the thermostatic expansion valve so that a high degree of superheat will be maintained until such time as the suction pressure in the system has been reduced by operation of the system.

Another object of my invention therefore is the prevention of overloading of a refrigeration system, as may occur upon initial starting up of the system, by adjusting the superheat setting of the thermostatic expansion valve to a relatively high value when the system is first placed in operation and then automatically reducing the superheat setting thereof.

A further object of my invention is to control the superheat setting of the expansion valve, in a system as just described, in response to variations in suction pressure in such manner that the superheat setting of the expansion valve is relatively high whenthe suction pressure is high and is reduced to the normal desired setting upon reduction in suction pressure.

More specifically, I prefer to'obtain this action by changing the temperature of the thermostatic element of the thermostatic expansion valve so that it is maintained at a temperature different than that at which it would be maintained solely by the flow of refrigerant through, the evaporator. This is preferably accomplished by applying additional cooling for the thermostatic element of the expansion valve and preferably by means of the same apparatus which is utilized to change the temperature of the thermostatic element of the expansion valve for varying the capacity of the refrigeration system at times other'than when the system is first placed into operation.

It is therefore another object of my invention both to maintain relatively high superheat upon an initial starting of the system and until such time as the suction pressure is reducedand to thereafter vary the capacity of the system in accordance with requirements all by the use of artificial or auxiliary cooling of the thermostatic element of the expansion valve by means of an auxiliary evaporator which obtains its refrigerant from the system under control.

Refrigeration systems are being used more and more, not only in test work but also in various industrial applications, for maintaining extremely low temperatures such as 100 F. At other times it is desired to operate the same refrigeration system at more normal temperatures, such as 0 F. It is a characteristic of commercial expansion valves of the thermostatic type that if set to maintain a desired superheatat say l00 F., and the system is then operated at 0 JFK, the expansion valve will maintain a much lower superheat at F. than it does at 100 F. This is an inadequacy in the expansion valves themselves as now commercially produced.

It is another object of the present invention to provide means for correcting this condition so that an expansion valve which is set to give a predetermined superheat when the system is operating at one suction pressure will maintain the same superheat even though the suction pressure at which the system is operating is changed over a relatively wide range.

It is a further object of this invention to accomplish the above results by adjusting the superheat setting of the thermostatic expansion valve automatically in response to changes in suction pressure, it being apparent that much lower suction pressures will be maintained at -100 F. than will be maintained when the system is controlling at '0 F.

More specifically, I prefer to accomplish this by varying the super-heat setting of the expansion valve through the application of auxiliary cooling in the manner heretofore explained.

Other objects of the invention will become apparent upon a reading of the following detailed description and by reference to the accompanying drawings, in which,

Fig. 1 discloses a refrigeration system the capacity of which is changed by applying variable cooling effects to the thermostatic element of a thermostatic expansion valve through the use of an auxiliary evaporator,

Fig. 2 discloses a system of control for the control valve of the apparatus in Figure 1' such that the capacity of the'system is varied in accordance with demand, overloading of the system is prevented upon initial starting of the same, and in which the super-heat maintained by the system may be held constantover wide ranges of suction pressure changes, and

Fig. 3 discloses a furthercontrol arrangement for maintaining constant superheat even though the suction pressure varies widely and in which the system cannot initially be started under a heavy load.

Referring first to Fig. 1, a compressor ill driven by an electric motor supplies compressed refrigerant to a condenser |2 by means of a pipe l3. The outlet side of the condenser I2 is connected to the inlet of a thermostatic expansion valve M by means of pipes I5 and I6. The outlet side of the thermostatic expansion valve I4 is connected to an evaporator I1 by a pipe l8 and the outlet of the evaporator I1 is connected to the suction side of the compressor by a suction pipe I9. The thermostatic expansion valve H is connected to the suction line l9 by the usual equalizer connection, 20 so that the pressure responsive. member of the thermostatic expansion valve responds to the actual pressure on the suction side of the system. In addition, the expansion valve I4 is provided with the usual thermostatic responsive mechanism herein shown as comprising a bulb 2| which is connected to the expansion valve by the usual connecting pipe 22. The bulb 2| responds to the temperature of the refrigerant in the suction line l9 and to this end may be attached to the pipe l9'in any of the manners common to the art.

The apparatus thus far described comprises the ordinary compression type refrigeration system. The evaporator I1 may be used for any desired purpose and is herein shown as located in a conditioning chamber 23 through which air may be blown in the usual manner for cooling any de- 4 sired room or space. Or the evaporator l1 could be located in a test box or could be utilized to cool a cold storage space or to cool any desired room or apparatus used in an industrial process.

The compressor motor may be controlled in any of the usual manners and is herein shown as controlled by a switching mechanism 24 which responds to suction pressure and head pressure, being connected to the suction line is by a pipe 25 and to the high pressure pipe i3 by a pipe 26. This mechanism may take any of the usual forms but is preferably of the type disclosed in the Carl G. Kronmiller application, Serial No. 371,001, filed December 20, 1940, now Patent No. 2,317,503, granted June 5, 1945.

In brderto modulatingly vary the capacity of the evaporator I1, I provide cooling means for the bulb 2| which preferably takes the form of a small auxiliary evaporator 21. This evaporator 21 is connected to the supply of liquid refrigerant between the expansion valve l4 and the condenser I2 by a pipe 28 that connects to the junction of pipes I5 and I6. Contained within the pipe 28 is an orifice 29 which restricts the flow of refrigerant to the auxiliary evaporator 21. side of the auxiliary evaporator 21 is shown connected to the suction line l9 by pipes 30 and 3| and a controlling valve 32. It could however be connected to the main evaporator coil |1 near its outlet end. The controlling valve 32 is utilized to modulate the flow of refrigerant through the evaporator 21 and may be controlled by any condition which is representative of the load on the system. It has herein been shown as controlled by a self contained volatile fluid room thermostat comprising a motor portion 33, a controlling bulb 34, and a connecting tube 35.

When the room is hot the control valve 32 is completely closed so that no refrigerant is flowing through the auxiliary evaporator 21. Under such conditions the cooling of the bulb 2| is due entirely to the temperature of the refrigerant in the suction line I9. The system is therefore operating as any ordinary refrigeration system operates and the evaporator H is operating at the capacity determined by the setting of the expansion valve. H. Such operation of the system at full capacity will begin lowering the room temperature.

Upon the first lowering in the room temperature the control valve 32 is opened very slightly. A small amount of refrigerant will now flow to the evaporator 21 and the pressure therein will depend upon the amount control valve 32 is open, the suction line pressure, etc. The initial opening of control valve 32 may not cause evaporator 21 to cool the bulb 2| below its original temperature. However, as soon as the control valve is opened sufficiently, the pressure in evaporator 21 and the amount of refrigerant flowing thereto will be sufficient to cause a small amount of additional cooling of the bulb 2|. The extra cooling or lowering in temperature of the bulb 2| will result in a further closure of the expansion valve l4 so that less refrigerant is fed to the evaporator l1. This will raise the superheat of the refrigerant in the suction line l9 and this increased temperature of the suction line l9 will react on the bulb 2| so as to raise'its temperature somewhat. The bulb 2| responds to temperature and cannot distinguish between the temperature condition resulting from the refrigerant in the suction line H! or the temperature condition resulting from the auxiliary evaporator 21 or the resultant temperature condition of these two.

The outlet On the other hand, when the winding 56 is gized sufilciently: more highly than the Winding Therefore, upon an initial fall in the room temperature the overall effect is to slightly raise the motor winding 41 and energizes the motor winding 48 through the condenser 43. This circuit is as followszstarting with'the lower end of secondary 66, wire .51, wire 68, switch arm contact 58, wire 68, switch arm HI, switch arm II, and

wire 12. The circuit then branches, one part goby additional heat in the suction line l9 through the medium of the thermostatic expansion valve 14 cutting down on the amount of refrigerant supplied to the evaporator H. In this manner. the capacity of the evaporator I1 is modulated in accordance with room temperature by modulating the supply of refrigerant to the auxiliary evaporator 21 for the thermostatic bulb 2| of the thermostatic expansion valve I4. As stated above, although I haves hown auxiliary evaporator 21 connected to the suction'line l9, it could instead be connected into the main evaporator ll at a point near its outlet end.

Turning now to Fig. 2, the control valve 32 is therein shown as being electrically controlled from a variable resistance modulating type of room thermostat generally indicated at 40. Those parts of the refrigeration system proper which correspond to'those of .Fig. 1 have been numbered in accordance with the numbering of Fig. 1. In Fig. 2, in addition, other control apparatus is disclosed to prevent. overloading of the system on an initial start and also to maintain substantially constant superheat in the system upon relatively wide changes in suction pressure,

ing directly through winding" and back to the upper end of transformer secondary 56 by way of wire 13 whereas the other portion goes through condenser 48 and winding 48 to wire 13 and back to the upper end of secondary 66. It will therefore be seen that the usual type of two phase circuit has been set up for the motor rotor 45 whereupon it will rotate in such a direction as to move valve 32 towards its closed position, it being shown in its fully open position. The switch arms 10 and II comprise one of the usual limit switches and limits movement. of the valve 32 in closing direction so as to stop further energization of the motor mechanism when the valve has been fully closed. When this occurs, the insu-' lating portion I4 of an arm secured to the final driven shaft 44, as at 15, engages switch arm II so as to move it away from-switch arm 18. Similarly, there is a limit switch comprised by switch arms 16 and 11 which limits the opening as will occur when the operating temperature of i the system is changed say from 0F. to 100 1".

The control valve 32 is provided with an operating stem 4| which in turn is connected to a rack 42 provided with teeth thereon. A pinion 43 cooperates with the rack 42, and is carried by the main shaft 44 of a 'motor mechanism which includes a motor rotor 45 and a reduction gearing generally indicated at 46. The rotor 45 is caused to rotate in reverse directions by windings 41 and 48 and a condenser 49 under the control of a relay mechanism 50.

The relay mechanism 50 includes an armature 5i pivoted at 52 and provided with legs '53 and 54 with which windings 55 and 56 cooperate. The armature 5| operates a switch-arm 5i which is carried by an insulating block 58. It will be obvious upon inspection of the showing of the relaythat when winding 55 is energized sufliciently more highly than winding 56, the switch arm 51 moves into engagement with a contact 59.

ener- 55, the switch arm 51 engages a contact 60. When these windings are substantially equally energized, as they are with the parts in the position shown in Fig. 2, the switch arm 51 is intermediate contacts 59 and 60 and is not engaging movement of the valve. Since the valve is shown in its full open position, .the insulating portion 14 is engaging the switch arm 11 so as to move it away from switch arm I6. However, assuming that the switch arms were in engagement and that the relay switch arm 51 engages contact 60, then circuits for the motor windings 41 and 48 are set up as follows: starting with the lower end of secondary 66, wire 61, wire 68, switch arm 51, contact 60, wire 18, switch arm 16, switch arm 11, and wire 19. At this point the circuit splits, one branch going directly through winding 48 to wire 13 and therefore back to the secondary 66,

whereas the other branch goes through condenser 49 to winding 41 and back to the secondary 66 by way of wire I3. It will now be seen that the other winding of the motor is directly energized whereas that winding which was formerly directly energized is nowenergized through the condenser 49. As a result, the motor rotor 45 will rotate in the reverse direction so as to drive the valve towards open position. It will thus be seen, that except when the motor means is in one or the other of its limiting positions, energization of winding 55 to a greater extent than winding 56 causes a closing movement of the control valve 32 whereas energization of the winding 56 more highly than winding 55 results in an opening movement of the control valve 32.

The relative energizations of the windings 55 and 56 are controlled by the room thermostat 40 (previously mentioned), by a suction pressure responsive variable resistance device 80, and by a second suction pressure responsive variable-resistance device 8|, as well as by a balancing po' tentiometer. prises a resistance 82 with which the contact portion 83 of the arm secured to shaft 44 at 15 cooperates. The arrangement is such that the contact portion 83 completely traverses the balanc ing resistance 82 when the control valve 32 moves from one of its extreme positions to its other extreme position.

The room thermostat 40 is shown in its fully expanded or hot position and comprises a bellows 84 which is anchored at one end and which has secured to its other end an operating member 85. The operating member 85 includes an The balancing potentiometer com- 7 upwardly extending portion 88 which cooperates with a control resistance 81. It also has a downwardly extending arm 88 which engages a switch arm 89 when the room thermostat is fully contracted in response to low temperature so as to move such switch arm 89 out of engagement .t'om a switch arm 90 to thereby deenergize the compressor motor II as will be evident upon an examination of the simple series circuit for such compressor motor. Movement of the bellows 84 is opposed by a relatively long light coil spring 9| which may be adjusted by means of a nut 92 threaded into a stationary portion of the apparatus shown at 93. As the nut 92 is screwed inwardly, the spring 9I is compressed more and more so that higher and higher temperatures will be required in the room in order to cause movement of the bellows to its fully expanded position in which it is shown.

The suction pressure responsive mechanism 80 is the one which maintains substantially con stant superheat when the system operates on widely difierent suction pressures. This mechanism includes a bellows 95 anchored at one end and having such end connected to the suction pipe I9 by pipes 98 and 91. I The other end of the bellows 95 operates a contact arm 98 which in turn cooperates with a relatively long but electrically small resistance 99. In addition, a relatively heavy short coil spring I00 opposes movement of the bellows 95 and to this end has one of its ends engaging the movable end of the bellows 95 and its other end engaging a stationary support IOI. This short heavy spring requires that the suction pressure vary over a wide range in order for contact arm 99 to completely traverse resistance 99. In other words, the mechanism 80 has a very wide differential.

The suction pressure responsive device 8I is the one which prevents operation of the refrigeration system at high capacity when the same is first placed in operation. This device includes a bellows I02 anchored at one end and having I v secondary 88 by the wire 13 and a wire IIO. The

upper end of balancing resistance 82 is connected to the upper end of winding 58 by a wire III whereas the lower end of such balancing resistance is connected to the upper end of winding 55 by a wire I I2. The lower end of winding 58 is directly connected to the right hand end of the room thermostat control resistance 81 by a wire H3. The lower end of winding 55 is connected to the left hand end of the room thermostat control resistance 81 through the resistances 99 and I05 by wires H4, H5, and H8. The contact arm 88 which cooperates with the room thermostat resistance 81 is connected to the lower end of secondary 88 by a wire I I1 and the wire 81.

Operation of Figure 2 With the parts in the position shown, the system is shut down since the line switch as well as a line switch I I8 in series with the compressor motor II are both open. As a result, the suction pressure of course is high so that bellows 95 and I02 are expanded and their respective contact arms 98 and I04 are at the extremeri-ght hand ends of the cooperating resistances 99 and I05. Likewise, the room temperature is high so that bellows 84 is expanded fully and the contact arm 88 is at the extreme left hand end of cooperating resistance 81. The control valve 32 is fully open and the balancing contact 83 is at the extreme lower end of balancing resistance 82.

To place the system in operation, the line switches and H8 are both closed. The compressor motor I I is thereupon energized by a circuit as follows: line wire II9, line switch H9, wire I20, switch arm 89, switch arm 90, wire I2I, the high and low pressure switch 24, wire I22, compressor motor II, wire I23, and line switch II8 to the other line wire I24. Also, the windings 55 and 58 are energized. The circuit for the winding 55 is as follows: from the upper end of secondary 68, wire 13, wire IIO, balancing contact arm 83, wire II2, winding 55, wire II4, all of resistance 99, contact arm 98, wire H5, all of resistance I05, contact arm I04, wire II8, contact arm 86, wire H1, and wire 81 to the lower end of secondary 88. The energizing circuit for winding 56 is as follows: from the upper end of secondary 86, wire 13, wire IIO, balancing contact arm 83, all of the balancing resistance 82, wire III, winding 58, wire H3, all of room thermostat-resistance 81, contact arm 88, wire H1, and wire 81 to the lower end of secondary 88. The resistance I05 should be approximately twice that of resistances 81 and 82 which in turn are equal to each other. The resistance 99 is much less. Therefore, the Winding 58 has somewhat less resistance in series with it than the winding 55 and is the more highly energized. Even if this were suflicient to move contact arm 51 into engagement with contact 60, nothing could happen since the circuit thus established is a valve opening circuit and the valve is already wide open with the limit switch arms 18 and 11 separated.

Upon starting of the compressor, liquid refrigerant is furnished to the main evaporator and also a maximum supply is furnished to the auxiliary evaporator since the control valve 32 is wide open. The thermostatic expansion valve is therefore operating under its highest superheat conditions so that very little, if any, refrigerant is permitted to flow to the evaporator. As a result, the system when it first starts up must start at a reduced capacity and cannot overload the compressor or compressor motor. As the system continues to operate however, the suction pressure will begin reducing. Upon a relatively small reduction, the long light spring I08 will substantially compress the bellows I02 so that contact arm I04 will move to the left along resistance I05 to out part of it out of the circuit of winding 55. This change in suction pressure however will not be sufficient to cause any appreciable movement of slider 98 along resistance 99.

The energization of winding 55 will therefore gradually increase and when slider I04 has moved part way along resistance I05, the energization of winding 55 will become great enough in respect to winding 58 to swing contact arm 51 into engagement with contact 59. The motor mechanism will thereupon be energized by the circuits previously traced so as to move valve 32 towards its closed position. As such movement takes place, the balancing contact arm 83 begins moving upwardly towards the top of balancing re- 9 sistance 82 to insert part of the balancing resistance in circuit with winding 55 and remove some of the balancing resistance from the circuit for winding 56. This will continue until the two relay windings 55 and 55 are again substantially equally energized so t atcontact arm 51 moves away from contact 59. This partial closing of control valve 32 reduces the supply of refrigerant to the auxiliary evaporator so that less auxiliary cooling is furnished to the bulb of thether mostatic expansion valve. This in effect reduces the superheat setting thereof so that more refrigerant is admitted to the evaporator and the system begins picking up the load. In this manner, as the suction pressure is reduced, the control valve 32 is moved closer and closer to its along resistance 99 so that substantially all of resistance 99 is still in the circuit. This prevents complete closing of control valve 32 for reasons which will soon appear.

With the room thermostat adjusted as shown wherein the spring 9| is fully expanded, that is, the adjusting nut 92 is screwed all the way out, the thermostat is set to operate at say -100' F. This means that the suction pressure will have to be reduced a great deal. As this suction presoperating at such controlling temperature, all of the resistance 99 will have been removed from the circuit. Under these conditions then, and until the temperature of the room or box lowers, the control valve 32 will be fully closed or substantially closed so that thesystem is operating at its full capacity. Under these conditions the thermal expansion valve is receiving no auxiliary cooling and will control to give a normal amount of superheat, due to its conventional adjustment, such as 10 degrees.

Now, as the room temperature begins to fall, the slider 85 will move along resistance 81 towards its right hand end. The circuit for winding 55 now includes all of the balancing resistance 82 but substantially little of the resistance 81, whereas the circuit for winding 55 includes none of the balancing resistance 82 but substantially all of the resistance 81. Then, as the-slider 85 moves to the right. so as to add some of the resistance 81 to the circuit for winding 55 and'remove some of it from the circuit for winding 55, winding 56 will become'more highly energized than winding '55 whereupon contact arm 51 will swinginto engagement with contact 58. This will energize the motor mechanism so as to move it back towards the open As it so moves,

be opened wider and wider so as to permit the the spring 9|.

valve. When the room temperature is down to the proper value, arm 88 will engage the extreme right hand end of resistance 81 and the control valve 32 will be completely opened with the balancing contact arm 88 in the position shown. Remembering that all of the resistance 99 as well as all of the resistance I05 has been cut out of the circuit, then we have a condition wherein winding 55 has all of the control resistance 81 in circuit with it and the winding 55 has all of the balancing resistance 82 in its circuit. Since these resistances are equal, the two windings are equally energized and the contact arm 51 is in its intermediate position shown. The system is now operating at its minimum capacity as explained in Fig. 1 under conditions where the control valve 3213 all the way open.

Now let us assume that it is desired to operate the room or box at a new temperature. Let us assume that this new temperature is 0 F. which .is much higher than the temperature theretofore maintained. The nut 92 of the room thermostat 48 is screwed in so as to greatly compress I As a result, the room tempera tureor box temperature must rise much higher than before in order for the bellows 84 to over come the spring 9|. Operating under these new conditions and assuming that the load on the system is such that the room thermostat is fully expanded, the suction pressure will rise materially but it will still be low enough so as to cut out all of resistance I05. However, due to the increase in suction pressure part or all of resistance 99 will now be reinserted into the circuit. Therefore, even with the room thermostat demanding all of the cooling possible, the valve 32 will not be fully closed since the winding 55 will now have the resistance 99, or part of it, in series with it. This means that the thermostatic expansion valve will be operating at a little higher superheat than it has been mechanically adjusted to maintain because a small amount of auxiliary cooling is taking place. .However, it is a well known characteristic of commercial expansion valves of the thermostatic type, that if set to maintain a normal superheat of 10F. while operating at a suction pressure so as 'to maintain 100 F., then if the system is operated at a higher suction pressure so as to maintain 0 F. without changing the mechanical setting'of the expansion valve, it will maintain a lower superheat than before. This is inherent in the construction of commercial thermostatic expansion valves of today. However, by reason of the insertion of resistance 99 so as to maintain the,

control valve 32 slightly open even when the room thermostat is demanding full cooling, the desired superheat of 10 F. will be maintained without the operator mechanically readjusting the thermostatic expansion valve.

From the foregoing, it will be seen that in Fig. 2 the room thermostat 40 of the variable resistance type, in combination with the electric motor mechanism, operates the control valve 32 in the same manner as the self contained room thermostat of Fig. 1. In addition, whenever the room thermostat is entirely satisfied and the room or box temperature has been reduced to the desired 'amount, the arm 88 moves switch arm 89 from engagement with contact 90 so as to shut down the compressor under such conditions. Furthermore, the suction pressure responsive device 8| is so correlated with the room thermostat 48 and the balance of the electrical system as to prevent initial operation of the system at h gh c 11 pacity until such time as the suction pressure has been reduced, thereby preventing overloading of the compressor and the compressor motor. In addition, the suction pressure responsive device 80 which responds fully only to a much lower suction pressure, modifies the action of the thermostatic expansion valve so as to maintain a desired amount of superheat irrespective of whether the system is operating at a relatively high suction pressure or at a very low suction pressure.

Turning now to Fig. 3, a further modification is shown by means of which constant superheat may be maintained in a refrigeration system even though it operates under widely fluctuating suction pressures. In addition, means are provided to prevent operation of the system at high capacity until such time as the suction pressure has been reduced a reasonable amount.

In Fig. 3, certain of the parts correspond to similar parts disclosed in Figs. 1 and 2 and have therefore been given the same reference characters. A refrigeration system is disclosed having the compressor I driven by the electrical motor II for delivering refrigerant to a condenser I2 by means of the pipe I3. The condenser I2 isconnected to the evaporator I1 by a pipe I30 which contains a valve I3I that is controlled in such a manner as to make it equivalent to the ordinary expansion valve. The evaporator I1 is in turn connected to the suction side of the compressor I0 by the suction line I9. The compressor motor I I may be controlled in any desired manner'as by the combined high pressure and suction pressure controller 24 previously explained in connection with Fig. 1. In addition, a room thermostat I32 may be included so that the compressor motor II is controlled by a circuit as follows: line wire I33, room thermostat I32, wire I34, controller 24, wire I35, compressor motor II, and the other line wire I29.

The valve I3I is positioned by an electric motor mechanism I36 which may be of the same general type disclosed .in Fig. 2. It therefore includes a main operating shaft 44 which drives a pinion 43. This pinion 43 cooperates with a rack I31 attached to a valve stem I38 for the valve I3I. In addition, the motor mechanism I36 drives a balancing potentiometer comprising the resistance 92 and, the contact arm 83. -The,,connection betweenthe final driven shaft 44 and the balancing contact arm 83 is herein shown as comprising a second pinion I39, also secured to the shaft 44, and a rack I40 with which such pinion I39 cooperates, the rack I40 in turn being connected to the balancing contact arm 83.

The motor mechanism I36 is energized for reverse rotation or for entirely stopping the same by the relay mechanism 59 which corresponds exactly to therelay mechanism of Fig. 2. Power for operating the motor mechanism I36 is supplied by a transformer I4I having a high voltage primary I42 and a low voltage secondary I43. One side of secondary I43 is connected to the switch arm 51 of the relay 50 by wires I44 and I45. The contacts 59 and 60 of such relay are connected to the motor mechanism I36 by wires I46 and I41. Further, the motor mechanism I36 is connected to the other side of the secondary I43 by wires I48 and I49.

. sistance 62.

In Fig. 3, such energization of the motor mech-f anism I36 is arranged to move valve I3I towards open position and to move balancing contact arm I 83 towards the left hand end of \balancing reing 55 is energized more highly than winding 56, switch arm 51 engages contact 59 to establish a motor circuit for driving the motor in the opposite direction as follows: secondary I43, wire I44, wire I45, switch arm 51, contact 59, wire I46, motor mechanism I36,wire I40, and wire I49 to the other side of secondary I43. Such reverse movement of the motor mechanism I36 drives the valve I3I towards closed position and moves the balancing contact arm 83 along resistance 82 towards its right hand end.

The motor mechanism I36 is controlled by a differential controller generally indicated at I50 and a suction pressure device I5I. The differential controller I50 is herein shown as including two thermostatic responsive devices. One of these comprises a bellows I52 connected to a bulb I53 by a tube I54. The bulb I53 is associated with the suction line I9 so as to respond to the temperature of the refrigerant after it has evaporated and become superheated. The right hand end of bellows I52 is secured to a fixed support I55 and the left hand end thereof is attached to an operating rod I56. For purposes of adjustment, a, spring I51 may be provided for opposing the expansion of the bellows I52. The second thermostatic responsive device of the differential controller I50 comprises a bellows I58, a controlling bulb I59, and a connecting tube I60. The bulb I59 is associated with the evaporator at a point where the refrigerant has no superheat so that 4 it responds to the temperature of the refrigerant at the prevailing suction pressure. The bellows I58 could respond to suction pressure, such as is usual in the refrigeration art, but there are certain advantages in having it respond to temperature and being in the form of a volatile flll type of thermostat as will be later explained. The bellows I58 has its left hand end secured to a support I6I and its right hand end is connected to the operating rod I56. A spring 262 may be provided for opposing expansion of the bellows I56.

The operating rod I56 is provided with a contact arm I 62 that cooperates with a resistance I63 and with a second contact arm I64 that cooperates with a resistance I65. It will be noted that the contact arms I62 and I64 are insulated from the main operating rod I56 so that these contact arms are electrically independent of each other.

The suction pressure responsive controller I5I includesa bellows I66 that is connected to the suction line I9 by a pipe I61. The right hand end of bellows I66 is anchored to a support I68 and its left hand end operates a contact arm I69 that cooperates with a resistance I10. A spring I1I may be provided to oppose the expansive movement of bellows I66 upon increase in suction pressure in order that the-instrument may be adjusted as desired. Also associated with the contact arm I69 is a pair of switch arms I12 and I13, the arrangement being such that upon high suction pressure and consequent movement of the contact arm I69 sufficiently far to the left, switch arm I12 is engaged and moved away from switch arm I13.

The remaining circuit connections will now be described. The upper end of relay coil 55 is connected to the contact arm I64 by a wire I15. The

Onthe other hand, when the windright hand end of resistance I65 which cooperates with the contact arm I64 is connected to the left hand end of resistance I by wires I16 and I 1,1. The lower end of relay coil 55 is connected to the left hand end of balancing resistance 82 by wires I 18 and I19. Similarly, the upper end of relay coil 56 is connected to the contact arm I62 by a wire I80. The cooperating resistance I63 is connected to switch arm I12 by a wire I8I and the cooperating switch arm I13 is connected to the right hand end of resistance I10 by wires I82 and I83. The lower'end of relay coil 56 is connected to the right hand end of balancing resistance 82 by wires I84 and I85. A resistance I86 is connected in parallel with the resistance I10 and in like manner a resistance I81 is connected in parallel with the balancing resistance 82. The purpose of these parallel connected resistances will be explained hereinafter.

Operation of Figure 3 For the moment, let us consider that the bellows I66 of the suction pressure controller I5I is disconnected from the contact arm I69 so that it-' come more than the predetermined desired amount higher than the temperature to which the bulb I59 responds. Bellows I52 will therefore exert an increased force in respect to bellows I58 and operating rod I56 will be shifted to the left.

This means that part of resistance I 63 is removed from the circuit of relay winding 56 and more of resistance I65 is insertedinto the circuit of relay winding 55. Winding 56 therefore becomes more highly energized than winding 55. The circuit for winding 56 under these conditions is as follows: from the left hand side of transformer secondary I43, wire I44, wire I90, contact arm I69, the right half of resistance I10, wire I83, wire I82, switch arm I13, switch arm I12, wire I8I, a small portion of resistance I 63, contact arm I62, wire I80, relay winding 56, wire I84, wire I85, the right hand half of balancing resistance 82, balancing contact arm 83, and wire I49 to the other side of secondary I43. The circuit for relay winding 55 is as follows: from the left hand side of secondary I43, wire I44, wire I90. contact arm I69, the left hand half of resistance I10, wire I11, wire I16, a relatively large portion of resistance I65, contact arm I 64, wire I15, relay winding 55, wire I 18, wire I19, the left hand half of balancing 14 in: movement of valve ill will cease. With valve I 3| opened to a wider position, more refrigerant is fed to the evaporator I1 so that the superheat is reduced. In other words, the temperature differential between the bulbs I53 and I59 is again brought back to the desired value. Thus, upon increasein the-superheat over the desired value,

- the operating rod I56 is moved further and further towards the left so thatmotor mechanism I36 opens the valve I3I further and further in the manner just described.

0n the other hand, upon a reduction in the superheat below the desired value so that the terriperature at bulb I53 is no longer as high above that of bulb I59'as desired, the main operating rod I56 will move towards the right. Now, part of resistance I65 in'series with winding 55 will be removed from such circuit and more of resistance I63 which is in series with winding 56 will be added to its circuit. Therefore, the winding 55 becomes more highly energized than the winding 56. Switch arm 51 thereupon engages contact 59 and motor mechanism I36 is driven in the reverse direction so as to move valve I3I towards its closed position. At the same time, the balancing contact arm 83 moves along balancing resistance 82 towards its right hand end so asto rebalance the energizations of windings 55 and 56.

, In this manner, with the parts thus far described wherein the suction pressure controller I5I is disconnected, the valve I3I is operated in the amount of superheat will decrease.

a manner which it would appear would maintain desired superheat under all conditions. However, the fact remains. that the superheat will vary considerably upon relatively wide changes in suction pressure. The reason for this is that the pressures produced bya volatile fill thermostat will not change equally upon equal changes in temperature at their controlling bulbs at different temperature levels. In other words, suitable fills for such thermostats are not such that the pres-' sures change in equal increments for equal temperature changes. This variation is not serious, when the suction pressure is only fluctuating over a few pounds. However, in low temperature refrigeration work, this does result in the maintenance of superheats which are not desired. In other words, if the apparatus is set so as to give a desired amount of superheat at low suction pressure, then asthe suction pressure increases,

The purpose of the suction pressure responsive device I5I is to correct this condition. The resistances I63 resistance 82, balancing contact arm 83 and wire I49 to the other side of secondary I43. Since relay coil 56 is now more highly energized than relay coil 55, switch arm 51 engages contact 60 to energize motor mechanism I36, in the manner previously described, whereupon valve I3I is opened further and balancing contact arm 83 moves along balancing resistance 82 towards its left hand end. Such movement increases the amount of resistance in series with winding 56 and decreases the amount of resistance in series with winding 55. Therefore, when suflicient movement has resulted, these windings will again be equally energized whereupon the motor mechanism I36 will be deenergized and further openand I are so chosen that their cooperating contact arms I62 and I 64 need only move over a rortion of such resistances in order to obtain complete opening and closing movements of the valve I3I. Thesuction pressure responsive device, by moving contact arm I69 along resistance I10, shifts the control point of the differential pressure responsive controller I50. In other words, while the same differential pressure change must take place in order to operate the valve I3I from full open to full closed position, the value of differential pressures at which such movements occur are shifted by the suction pressure responsive controller I5I.

With the parts in the position shown let us assume there is a substantial increase in suction pressure but that the superheat remains the same. The temperature at bulbs I53 and I59 will both therefore rise but they will rise to the same extent. However, bulb I53 is responding to a higher temperature than bulb I59, since it is superheat.

15 responding to the superheat. Bulb I53 is therefore operating on a different part of the vapor expansion curve of the fluid with which it is charged than is bulb I59. On this higher part of the curve, the pressure increase per degree of temperature rise is greater than on the lower part of the curve. The result is therefore that even though the temperatures at bulbs I53 and I59 have risen to the same extent, the increase in pressure in bellows I52 has been greater than the increase in pressure in the bellows I58. The differential pressure controller I50 will therefore have its main operating rod I56 moved to the left Just as though there had been an increase in the In other words, insofar as the differential pressure controller I50 is concerned, it believes there has been an increase in superheat when actually there has been none. Therefore, were it not for the suction pressure controller I I, the valve I3I would be opened further as previously explained due to taking part of the resistance I63 out of the circuit for winding 56 and.

inserting more of the resistance I65 into the circuit for winding 55. However, this rise in suction pressure also causes bellows I66 of the suction pressure device I5I to expand and move contact arm I69 to the left along resistance I10. Such movement adds resistance to the circuit for winding 56 and removes resistance from the -circuit for winding 55. By properly proportioning the various resistance values, these increases and decreases may be made to offset each other so that windings 55 and 56 remain equally energized. The valve I3I therefore remains in the same position and the ultimate result has been to merely shiftthe control point of the differential controller I50.

If, on the other hand, the suction pressure should be materially reduced and the superheat should remain the same, the temperature of both bulbs I53 and I59 would be reduced to the same extent. However, the pressure in bellows I52 would be reduced to a greater extent than the pressure in bellows I58 for the reasons pointed out above, and the operating rod I56 would move to the right thinking that there had been a decrease in superheat. The valve I3I would therefore tend to close so as to counteract this apparent decrease in superheat. However, at the same time the suction pressure device I5I would have its bellows I66 contract so that contact arm I69 moves along resistance I to the right and counteract the movement of operating rod I56. In this manner, constant superheat may be maintained upon wide fluctuations in suction pressure.

As stated above, the bellows I58 could be connected directly to the suction line as is common practice instead of being connected to the thermostaticbulb I59. However, if this were done, the response of the mechanism would be much smaller since the pressure curve for the well known refrigerants has a much slower rise when plotted against temperature than does the fluids ordinarily used in volatile fluid thermostats. For this reason, and particularly in low temperature refrigeration work where it is desired to maintain constant superheats over relatively wide ranges, the construction of the apparatus is simpler and a better response may be obtained by the use of two temperature responsive bulbs instead of the usual temperature responsive bulb and suction pressure responsive connection. However, either would work.

The motor mechanism I 36 is a standard commercial product in which the balancing resistance B2 is built into as a standard part of the equipment. This balancing potentiometer or resistance has a resistance of ohms. Likewise, differential controllers of the type indicated at I50 are a standard product in which each of the resistances I63 and I65 are 135 ohms. Likewise, suction pressure devices such as I5I are standard products in which the resistance I10 has a resistance of 135 ohms. It will be evident that if the differential controller I50 is to cause the complete movement of the motor mechanism I36 without the contact arms I62 and I64 traversing the colnplete resistances I63 and I65, these resistances must be greater than thebalancing resistance 82 and the resistance I10. Therefore, instead of changing a commercial product and inserting a new resistance therein, it is much simpler to reduce the effective resistance of the resistances 82 and I10 by connecting in the parallel resistances I81 and I86. Also, this provides a simple way by means of which the amount of correction given to diiferential controller I50 for a given movement of suction responsive controller I5I may be varied. It is only necessary to substitute different parallel resistance I86. Therefore, if a smaller resistance is substituted at I86, the correcting or compensating eifect of the suction pressure responsive controller I5I can be increased. By doing this, upon high suction pressures over-correction can be obtained so as to prevent the refrigeration system from operating at full capacity when the suction pressure is relatively high thereby preventing overloading of the compressor. Also, the switch I12, I13 is arranged to be opened upon high suction pressure and this interrupts the circuit for relay winding 56 which is the opening circuit for valve I3I. In this manner, the valve I3I may be compelled to completely close until the suction pressure has been reduced to some predetermined desired value thereby preventing any loading of the compressor upon extremely high suction pressure. With the valve I3I closed, operation of the compressor would soon reduce the suction pressure whereupon switch arm I12 will engage switch arm I13 and put the system into normal operation.

It will be obvious that many changes and modifications may be made in the various forms of the invention herein disclosed without departing from the fundamental concept thereof and I therefore intend to be limited only in view of the scope of the appended claims.

I claim as my invention:

1. In a refrigeration system having an evaporator, in combination, an expansion valve in control of the flow of refrigerant to the evaporator and including a thermostatic element responsive to the temperature of the refrigerant leaving the evaporator, an auxiliary evaporator associated with the thermostatic element of the expansion valve for cooling the same to vary the superheat maintained at the outlet of said evaporator by the expansion valve, conduit means for supplying refrigerant to said auxiliary evaporator from the main system from a point upstream of the main evaporator, restrictor means in said conduit means, and means including a valve arranged to prevent or establish the discharge of refrigerant from the auxiliary evaporator.

2, In a refrigeration system having an evaporater, in combination, an expansion valve in control of the flow of refrigerant to the evaporator and including a thermostatic element responsive 'to the temperature of the refrigerant leaving the evaporator, an auxiliary evaporator associated with the. thermostatic element of the expansion valve for cooling the same to vary the superheat maintained at the outlet of said evaporator by 3. In a refrigeration system, an evaporator, means for supplying refrigerant, thereto, an expansion valve in control of the supply of refrigerant to the evaporator, said expansion valve including a thermostatic element responsive to the temperature of the refrigerant leaving the evapo-' rator, pipe means for conducting refrigerant from the refrigerant supply in heat transfer relationship to said thermostatic element and returning it tothe system downstream of the evaporator, valve means for modulating the flow of refrigerant through said pipe means, and means re-' sponsive to the suction pressure in the system to prevent closing of said valve means if the suction pressure is too high.

4. In a refrigeration system, an evaporator, means for supplying refrigerant thereto, an expansion valve in control of the supply of refrigerant to the evaporator, said expansionvalve including a thermostatic element responsive to the temperature of the refrigerant leaving the evaporator, pipe means for conducting refrigerant from the refrigerant supply in heat transfer relationship to said thermostatic element and returning it to the system downstream of the evaporator, valve means for modulating the flow of refrigerant through said pipe means, temperature responsive means in control of said valve means for closing the same upon rise in temperature, and means responsive to the suction pressure in the system to prevent closing of the valve means if the suction pressure is above a predetermined value.

5. In a refrigeration system, an evaporator,

means for supplying refrigerant thereto, an expansion valve in control of the supply of refrigerant to the evaporator, said expansion valve including a thermostatic element responsive to the temperature of the superheated refrigerant leaving the evaporator, pipe means .by-passing the evaporator and expansion valve for conducting refrigerant from the refrigerant supply in heat transfer relationship to said thermostatic element and returning it to the system downstream of the evaporator, adjustable valve means for controlling the flow of refrigerant through said pipe means, and means responsive to thesuction pressure in the system to open said valve means upon rise in suction pressure to an extent such as to maintain the superheat of the, refrigerant leaving the evaporator constant upon such wide variations in suction pressure that the superheat would normally .vary.

valve means for, modulating the flow of refrigerant through said pipe means, and means responsive to suction pressure to maintain said valve means open suiliciently to reduce the flow of refrigerant through the evaporator to a safe value, when the suction pressure is so high that the system would otherwise be overloaded.

7. In a refrigeration system including an evaporator, in combination, thermostatic expansion valve means in control of the flow of refrigerant to the evaporator for normally maintaining a predetermined superheat of the refrigerant leaving the evaporator, auxiliary means to change the temperature of the temperature responsive portion of the thermostatic expansion valve means to a value other than would be obtained by the temperature of said evaporator alone, and means responsive to suction pressure to control said auxiliary temperature changing means to cause a high superheat to be maintained when the suction pressure is high.

8. In a refrigeration system adapted to have its suction pressure varied over relatively wide ranges, an evaporator, thermostatic expansion valve means in control of the flow of refrigerant to said evaporator, the superheat of said refrigerant at the outlet of said evaporator normally varying for a single setting of said thermostatic expansion valve means upon such relatively wide variations in the suction pressure, auxiliary temperature changing means 'for affecting the thermostatic portion of said thermostatic expansion valve means so that its temperature is other than it would be due to the action of the evaporator alone, and means operated in response to suction pressure for controlling said auxiliary temperature changing means to vary the temperature of thethermostatic portion of said thermostatic expansion valve means so as to maintain a constant superheat of said refrigerant at said outlet of the evaporator upon wide fluctuations in suction pressure.

9. In a refrigeration system having an evaporator and a valve in control of the'flow of refrigerant thereto, in combination, differential pressure responsive means in control of said valve, said differential pressure responsive means including a fluid fill type thermostat responsive to the temperature of the refrigerant leaving the evaporator for producing one of the pressures for saiddiflerential pressure responsive means, the fluid fill being such that the pressures produced thereby vary unequally upon equal changes in temperature, the other of said pressures being varied upon changes in the pressure of the refrigerant in said evaporator, and means responsive to suction pressure for varying the response of said differential pressure responsive means to maintain the superheat of the refrigerant leaving said evaporator constant irrespective of the unequal pressure changes produced by said fluid fill type thermostat upon equal temperature changes.

10. In a refrigeration system having an evapothe refrigerant leaving said evaporator after it a 19 has become superheated and the other responding to the temperature of the evaporated refrigerant before it becomes superheated, whereby upon fluctuations in suction pressure varying superheats would be maintained by said pressure differential responsive means by reason of the unequal changes in pressure produced by said thermostats upon equal changes in temperature, and means responsive to the suction pressure for modifying the action of said diflerential pressure ing means for said electric circuit, and'a pair of fluid filled thermostats for producing opposing pressures to control said circuit adjusting means, said fluid filled thermostats each having a similar fill, one of said thermostats responding to the temperature of the refrigerant leaving said evaporator after it has become superheated and the other responding to the temperature of the evaporated refrigerant before it becomes superheated.

12. In a refrigeration system having an evaporator and a valve in control of the flow of refrigerant thereto, in combination, differential pressure responsive means in control of said valve, said differential pressure responsive means including a fluid fill type thermostat responsive to the temperature of the refrigerant leaving the evaporator for producing one of the pressures for said difi'erential pressure responsive means, the fluid flll being such that the pressures produced thereby vary unequally for equal changes in temperature, the other of said pressures being varied upon changes in the pressure of the refrigerant in said evaporator, and means responsive to suetion pressure for varying the response of said differential pressure responsive means upon increase in suction pressure to maintain the superheat of the refrigerant leaving said evaporator higher than it would otherwise be.

13. In a refrigeration system having an evaporator and a valve in control of the flow of refrigerant thereto, in combination, means in control of said valve to control the superheat of the refrigerant leaving the evaporator, said valve controlmeansincluding a fluid fill type thermostat responsive to the temperature of the refrigerant leaving the evaporator for producing a pressure for controlling said valve control means, the fluid fill being such that the pressures produced thereby vary unequally for equal changes in temperature, means responsive to suction pressure for varying the action of said valve control means to maintain the superheat of the refrigerant leaving said evaporator constant irrespective of the unequal pressure-changes produced by said fluid flll type-thermostat upon equal temperature changes, and means operable in response to a predetermined suction pressure for increasing the amount of said superheat during the initial operation of said system.

14. For use in a refrigerating system to controlthe action of a thermostatic expansion valve having a thermostatic bulb element in heat exchange relation to a portion of said system; control means comprising, in combination, an auxiliary evaporator arranged to be associated in heat exchange relation to said bulb element, said evaporator having an inlet and an outlet, restrictor means in said inlet, and valve means controlling said outlet.

15. In a refrigerating system including an evaporator and a valve for controlling refrigerant flow through the evaporator, in combination, electrically operated actuating means for said valve, first means for responding to the temperature of the evaporator at a location wherein liquid refrigerant is present, second means for responding to the temperature at the outlet of said evaporator, and electric circuit means controlled by said first and second temperature responsive means for regulating said actuatin means.

16. Control means for a refrigerating apparatus of the type including an evaporator and an expansion valve comprising, in combination, expansion valve motor operator means, follow-up means adjustable by said operator means, means for responding to evaporator outlet temperature including a variable resistor, means for responding to evaporator temperature at an intermediate location and including a variable resistor, electrical circuit means including said follow-up means and both of said resistor means, and relay means controlled by said electrical circuit means and arranged to control said operator means in a manner to maintain predetermined differences in temperature between said outlet temperature responsive means and said intermediate temperature responsive means.

17. In a refrigerating system of a sort wherein its suction pressure may vary over a relatively wide range and including a thermostatic expansion valve and an evaporator, said expansion valve being arranged to control refrigerant flow through said evaporator and having a thermostatic element arranged to respond to the temperature of refrigerant leaving said evaporator, an auxiliary cooling means in heat exchange relation with said thermostatic element, and control means for said auxiliary cooling means, said control means including means responsive to the suction pressure of said system.

' ALWIN B. NEWTON.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,987,948 Smith Jan. 15, 1935 2,056,401 Hoesel Oct. 6, 1936 2,258,485 Lange Oct. 7, 1941 2,280,425 Sanders Apr. 21, 1942 2,291,898 Holmes Aug. 4, 1942 2,313,391 Newton Mar. 9, 1943 2,319,993 Kaufman May 25, 1943 2,353,240 Huggins July 11, 1944 2,377,503 Kronmiller June 5, 1945 

